US20030216213A1 - Reduction gear and product group of reduction gears - Google Patents

Reduction gear and product group of reduction gears Download PDF

Info

Publication number
US20030216213A1
US20030216213A1 US10/400,063 US40006303A US2003216213A1 US 20030216213 A1 US20030216213 A1 US 20030216213A1 US 40006303 A US40006303 A US 40006303A US 2003216213 A1 US2003216213 A1 US 2003216213A1
Authority
US
United States
Prior art keywords
gear
planetary gear
reduction
low
tooth profile
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/400,063
Other languages
English (en)
Inventor
Akira Yamamoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Heavy Industries Ltd
Original Assignee
Sumitomo Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd
Assigned to SUMITOMO HEAVY INDUSTRIES, LTD. reassignment SUMITOMO HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YAMAMOTO, AKIRA
Publication of US20030216213A1 publication Critical patent/US20030216213A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H2001/2881Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H57/033Series gearboxes, e.g. gearboxes based on the same design being available in different sizes or gearboxes using a combination of several standardised units
    • F16H2057/0335Series transmissions of modular design, e.g. providing for different transmission ratios or power ranges

Definitions

  • the present invention relates to a reduction gear and a series of reduction gears, and more particularly to a reduction gear and a series of reduction gears capable of ensuring a region of a low reduction ratio of 1/2 to 1/30 with high efficiency while securing a large space at the center.
  • a reduction gear includes an input shaft, a reduction mechanism portion that slows down rotations of the input shaft, and an output shaft that outputs rotations slowed down by the reduction mechanism portion to a machine at the other end.
  • manufacturers providing reduction gears prepare a wide variety of types of reduction gears with different torques or reduction ratios as a series (a product group).
  • the arrangement or the construction of a series has an extensive influence on the characteristics and the cost of the entire series, and consequently, it has a direct influence on the appeal and the cost of individual reduction gears as a product.
  • a reduction gear GI of this type includes an input shaft 500 , an external gear (planetary gear) 504 allowed to wobble eccentrically about the input shaft 500 , and an internal gear 506 internally engaged with the external gear 504 , and (in general) components equivalent to rotations of the external gear 504 on its axis are taken out to a carrier end 508 by fixing the internal gear 506 , with which an output shaft 502 is rotated.
  • the K-H-V type reduction gear is generally used in a region of a high reduction ratio where the reduction ratio is higher than approximately 1/30, and in order to achieve a reduction ratio in a region lower than the above specified region, not only a special design is needed, but also an eccentric quantity e of the external gear 504 is increased, which poses a problem that it becomes more difficult to form a large hollow space at the center.
  • a first shaft 602 linked to a sun gear 604 is generally used as the input shaft, while either a carrier 606 or a second shaft 610 linked to an internal gear 608 is used as the output shaft.
  • a reduction gear G 2 of this type the upper limit of a reduction ratio as a single reduction gear is 1/5 to 1/7 approximately, and in order to obtain a reduction ratio higher than the limit, a double reduction gear is needed.
  • the dimension in the axial direction is increased, which in turn increases the cost.
  • FIG. 6C shows the skeleton of a structure of a reduction gear G 3 of this type.
  • the reduction gear G 3 includes a first shaft 700 , a carrier 704 linked to the first shaft 700 , a first planetary gear 708 and a second planetary gear 706 both supported rotatably by the carrier 704 , a first internal gear 710 engaged with the first planetary gear 708 , a second internal gear 712 engaged with the second planetary gear 706 , an output shaft 702 , and second and third shafts 714 and 716 linked to the first and second internal gears 710 and 712 , respectively.
  • the reduction gear G 3 has a complicated structure, but in turn it has an advantage that a reduction (step-up) gear can be formed in various manners.
  • the reduction gear G 3 of the 2K-H-III type omits a sun gear, and therefore, it is relatively easy to from a large hallow portion at the center.
  • the reduction gear G 3 of the 2K-H-III type has a narrow region where a reduction ratio can be arranged, and it is practically impossible to cover the entire region from 1/2 to 1/30 with the 2K-H-III type.
  • the invention was devised in view of the conventional problems, and therefore, has an object to provide a reduction gear and a series (a product group) of reduction gears having concentric input and output shafts, capable of securing a large hollow space at the center, and, in particular, being highly efficient with the ability to fully cover a region with a reduction ratio of 1/2 to 1/30 as needed.
  • the invention solves these problems with a reduction gear, including: an input shaft; a reduction mechanism portion for slowing down a rotation of the input shaft; and an output shaft for outputting the rotation slowed down by the reduction mechanism portion to a mating machine, wherein: the output shaft is hollow; the input shaft and the output shaft are placed coaxially; the reduction mechanism portion comprises a planetary gear mechanism including a carrier linked to the input shaft, first and second planetary gears supported by the carrier to be rotatable at a same rotational speed, a first internal gear engaged with the first planetary gear and maintained in a fixed state, and a second internal gear engaged with the second planetary gear and linked to the output shaft; and at least one of the first and second planetary gears has a trochoid tooth profile as a tooth profile, and the gear engaged with the planetary gear having the trochoid tooth profile has an arc tooth profile.
  • the invention also solves these problems with a reduction gear, including: an input shaft; a reduction mechanism portion for slowing down a rotation of the input shaft; and an output shaft for outputting the rotation slowed down by the reduction mechanism portion to a machine at the other end, wherein: the output shaft is hollow; the input shaft and the output shaft are placed coaxially; the reduction mechanism portion is composed of a planetary gear mechanism including a carrier linked to the input shaft, first and second planetary gears supported by the carrier to be rotatable at a same rotational speed, a first internal gear engaged with the first planetary gear and maintained in a fixed state, and a second internal gear engaged with the second planetary gear and linked to the output shaft; and at least one of the first and second planetary gears has an arc tooth profile as a tooth profile, and the gear engaged with the planetary gear having the arc tooth profile has a trochoid tooth profile.
  • these problems are solved by basically having a reduction mechanism of a so-called 2K-H-III type in order to achieve the region of a high reduction ratio (for example, 1/30 to 1/5), and by having a trochoid tooth profile as a tooth profile of at least one of the first and second planetary gears and having an arc tooth profile as a tooth profile of the gear engaged with the planetary gear having the trochoid tooth profile, or, by having an arc tooth profile as a tooth profile of at least one of the first and second planetary gears and having a trochoid tooth profile as a tooth profile of the gear engaged with the planetary gear having the arc tooth profile.
  • the first and second planetary gears have an equal number of teeth
  • the first and second internal gears respectively engaged with the first and second planetary gears have different numbers of teeth
  • a set of the first planetary gear and the first internal gear and a set of the second planetary gear and the second internal gear have different tooth profiles
  • the invention can be developed to a series (a product group) of reduction gears including a reduction gear as a component, the reduction gear including: an input shaft; a reduction mechanism portion for slowing down a rotation of the input shaft; and an output shaft for outputting the rotation slowed down by the reduction mechanism portion to a machine at the other end, wherein: the output shaft is hollow; the input shaft and the output shaft are placed coaxially; the series is divided into a high-side reduction gear group and a low-side reduction gear group responsible for a region of a high reduction ratio and a region of a low reduction ratio, respectively; the reduction mechanism portion of the high-side reduction gear group is composed of a high-side planetary gear mechanism including a high-side carrier linked to the input shaft, high-side first and second planetary gears supported by the high-side carrier to be rotatable at a same rotational speed, a high-side first internal gear engaged with the high-side first planetary gear and maintained in a fixed state, and a high-side
  • FIG. 1 is a cross section taken along the line I-I of FIG. 2, showing an overall arrangement of a high-side reduction gear according to one embodiment of the invention
  • FIG. 2 is a front view showing a structure of the high-side reduction gear when viewed from a direction II indicated by an arrow on the left side of FIG. 1;
  • FIG. 3 is a cross section taken along the line III-III of FIG. 4, showing an overall arrangement of a low-side reduction gear according to one embodiment of the invention
  • FIG. 4 is a front view showing a structure of the low-side reduction gear when viewed from a direction IV indicated by an arrow on the left side of FIG. 3;
  • FIG. 5 is a view showing a skeleton of a reduction mechanism of a 2K-H type.
  • FIG. 6A through FIG. 6C are views showing skeletons of reduction mechanisms of a K-H-V type, a 2K-H-I type, and a 2K-H-III type, respectively.
  • FIG. 1 is a sectional side view of a reduction gear (high-side reduction gear) according to one embodiment of the invention
  • FIG. 2 is a front view showing a structure of the high-side reduction gear when viewed from a direction II indicated by an arrow of FIG. 1.
  • FIG. 3 is sectional side view of a low-side reduction gear forming a series (a product group) of reduction gears according to one embodiment of the invention
  • FIG. 4 is a front view showing a structure of the low-side reduction gear when viewed from a direction IV indicated by an arrow of FIG. 3.
  • a series of reduction gears having these reduction gears as components is arranged in such a manner that a high-side reduction gear 100 is responsible for the region of a high reduction ratio (herein, 1/30 to 1/5) and a low-side reduction gear 200 is responsible for the region of a low reduction ratio (herein, 1/5 to 1/2).
  • the high-side reduction gear 100 belongs to a speed reduction mechanism referred to generally as a 2K-H-III type, and chiefly comprises an input shaft 102 , a high-side carrier 106 linked to the input shaft 102 , high-side first planetary gear 108 and second planetary gear 110 supported by the high-side carrier 106 to be rotatable about the input shaft 102 at the same rotational speed, a high-side first internal gear 112 engaged with the high-side first planetary gear 108 and maintained in a fixed state, a high-side second internal gear 114 engaged with the high-side second planetary gear 110 and linked to an output shaft 104 , and the output shaft 104 .
  • the input shaft 102 and the output shaft 104 use a line L 1 of FIG. 1 as their respective axial centers, and are placed coaxially.
  • the high-side first planetary gear 108 and second planetary gear 110 have an equal number of teeth, and each have a tooth profile of a smooth curve based on a trochoid.
  • the high-side first planetary gear 108 and second planetary gear 110 are integrated with each other through a carrier pin 120 , and supported rotatably by the high-side carrier 106 through a bearing 130 .
  • the high-side first internal gear 112 and second internal gear 114 are provided with a plurality of rotatable pins 122 , each of which forms an arc tooth profile.
  • the high-side second internal gear 114 is integrated with the output shaft 104 on the peripheral rim of a flange portion 104 a of the output shaft 104 .
  • the output shaft 104 includes a hollow portion S 1 , and is supported by a cross roller 128 placed between a front casing 132 and a relay casing 134 to be rotatable with respect to the casings 132 and 134 .
  • the flange portion 104 a of the output shaft 104 itself serves also as a cover that covers the front surface opening of the high-side reduction gear 100 .
  • the input shaft 102 is solid herein. It should be appreciated, however, that it can be readily made hollow depending on its application, and it is also possible to form a hollow space penetrating through the input and output shafts 102 and 104 .
  • An oil seal 126 is disposed between the flange portion 104 a of the output shaft 104 and the front casing 132 , and it seals oil in the reduction mechanism portion.
  • the high-side carrier 106 linked to the input shaft 102 starts to rotate, which in turn rotates the high-side first planetary gear 108 supported rotatably by the high-side carrier 106 .
  • the high-side second planetary gear 110 integrated with the first planetary gear 108 through the carrier pin 120 starts to rotate at the same speed.
  • the rotation of the high-side second planetary gear 110 is transmitted to the high-side second internal gear 114 , and outputted as being transmitted further to the output shaft 104 integrated with the high-side second internal gear 114 .
  • the low-side reduction gear 200 will now be explained in detail with reference to FIG. 3 and FIG. 4. A detailed explanation will be omitted for the portions structured in the same manner as those in the high-side reduction gear 100 for ease of explanation.
  • the low-side reduction gear 200 belongs to a reduction mechanism referred to generally as a 2K-H-IV type, and chiefly comprises an input shaft 202 , a low-side sun gear 206 linked to the input shaft 202 , a low-side carrier 207 maintained in a fixed state, a low-side first planetary gear 208 supported rotatably by the low-side carrier 207 and engaged with the sun gear 206 , a low-side second planetary gear 210 also supported rotatably by the low-side carrier 207 and rotating at the same rotational speed of the low-side first planetary gear 208 , a low-side internal gear 214 engaged with the low-side second planetary gear 210 and linked to an output shaft 204 , and the output shaft 204 .
  • the input shaft 202 and the output shaft 204 use a line L 2 of FIG. 3 as their respective axial centers, and are placed coaxially.
  • the low-side first planetary gear 208 and second planetary gear 210 have an equal number of teeth, and each have a tooth profile with a smooth curve based on a trochoid. Consequently, these components are designed in such a manner that not only the high-side first planetary gear 108 and the low-side first planetary gear 208 are used commonly, but also the high-side second planetary gear 110 and the low-side second planetary gear 210 are used commonly, and therefore, each can be used commonly in the high-side reduction gear 100 and the low-side reduction gear 200 .
  • the low-side first planetary gear 208 and second planetary gear 210 are integrated with each other through a carrier pin 220 , and are supported rotatably by the low-side carrier 207 through a bearing 230 .
  • the sun gear 206 includes a number (as many as teeth) of ring-like grooves 206 a on the periphery, and a rotatable pin 206 b used to form an arc tooth profile is incorporated in each. Also, by providing the low-side internal gear 214 with a plurality of rotatable pins 222 , the same arc tooth profile as that of the high-side second gear 114 described above is formed, and therefore, the low-side internal gear 214 and the high-side second internal gear 114 are designed in such a manner that they can be used commonly in the high-side reduction gear 100 and the low-side reduction gear 200 .
  • the low-side internal gear 214 is integrated with the output shaft 204 on the periphery rim of a flange portion 204 a of the output shaft 204 .
  • the input shaft 202 can be either solid or hollow.
  • the high-side carrier 106 and the low-side carrier 207 are also designed in such a manner that they can be used commonly. A function of the low-side reduction gear 200 will now be explained.
  • the revolution of the carrier pin 220 is limited (fixed)
  • the rotation of the low-side second planetary gear 210 is slowed down for a ratio of the number of teeth of the low-side second planetary gear 210 and those of the low-side internal gear 214 , then transmitted to the low-side internal gear 214 , and outputted as being transmitted further to the output shaft 204 integrated with the low-side internal gear 214 .
  • the high-side reduction gear 100 is adopted for the region of a high reduction ratio (1/30 to 1/5), while the low-side reduction gear 200 is adopted for the region of a low reduction ratio (1/5 to 1/2), and hollow shafts are used as the output shafts 104 and 204 in the respective gears.
  • the output shaft 104 of the high-side reduction gear 100 and the output shaft 204 of the low-side reduction gear 200 , the high-side second internal gear 114 and the low-side internal gear 214 , the high-side carrier 106 and the low-side carrier 207 , the high-side first planetary gear 108 and the low-side first planetary gear 208 , and the high-side second planetary gear 110 and the low-side second planetary gear 210 are made as components that can be used commonly, an increase in variety of components can be minimized, and it is thus possible to design a series with low inventory costs.
  • a tooth profile with a smooth curve based on a trochoid is adopted for the high-side first planetary gear 108 and second planetary gear 110 in the high-side reduction gear 100 , and an arc tooth profile is formed on the high-side first internal gear 112 and second internal gear 114 respectively engaged with the high-side first planetary gear 108 and second planetary gear 110 by providing a plurality of rotatable pins 122 and 123 , respectively. That the numbers (the numbers of teeth) and the diameters (tooth profile) are slightly different between the pins 122 and 123 .
  • the high-side first planetary gear 108 and second planetary gear 110 have an equal number of teeth but have slightly different tooth profiles.
  • the low-side first planetary gear 208 and second planetary gear 210 in the low-side reduction gear 200 have a trochoid tooth profile, and an arc tooth profile is formed on the sun gear 206 and the low-side internal gear 214 respectively engaged with the low-side first planetary gear 208 and second planetary gear 210 by providing a plurality of rotatable pins 206 b and 222 , respectively.
  • FIG. 5 shows one of skeletons of a reduction mechanism referred to generally as a 2K-H type, and this reduction mechanism includes an input shaft 300 , an output shaft 302 , a driving-end gear 304 , an output-end gear 308 , and a planetary gear 306 that engages with the driving-end gear 304 and the output-end gear 308 .
  • X 1 is working efficiency between the driving-end gear 304 and the planetary gear 306
  • X 2 is working efficiency between the output-end gear 308 and the planetary gear 306
  • i is a reduction ratio (the number of teeth of the output-end gear 308 /the number of teeth of the driving-end gear 304 ).
  • working efficiency between a pair of gears is a function of a coefficient ⁇ of friction on the tooth flank, which is known to be highly susceptible to a slipping velocity between the tooth flanks.
  • ⁇ of friction on the tooth flank which is known to be highly susceptible to a slipping velocity between the tooth flanks.
  • the lower the slipping velocity the greater the coefficient ⁇ of friction on the tooth flank becomes, which results in a reduction of the working efficiency.
  • this embodiment adopts the trochoid tooth profile and the arc tooth profile composed of a plurality of rotatable pins instead of the typical involute tooth profile, and coefficient ⁇ of friction on the tooth flank is reduced by increasing the slipping velocity in engagement through the use of rotations of the pins forming the arc tooth profile.
  • a significant advantage can be achieved by, in particular, adopting rotatable pins as the arc tooth profile.
  • the high-side first planetary gear 108 and the high-side second planetary gear 110 in the high-side planetary gear mechanism have an equal number of teeth; the high-side first and second internal gears 112 and 114 respectively engaged with the high-side first and second planetary gears 108 and 110 have different numbers of teeth; and a set of the high-side first planetary gear 108 and the high-side first internal gear 112 and a set of the high-side second planetary gear 110 and the high-side second internal gear 114 have different tooth profiles (pin diameters), it is still possible to form a so-called magical gear mechanism by adopting a combination of the arc tooth profile and the trochoid tooth profile, which are different from the involute tooth profile in that a shift manipulation is impossible, and a large reduction ratio can be thus obtained. Moreover, as has been described above, efficiency can be improved drastically in comparison with a magical gear mechanism based on the involute tooth profile.
  • a series may be formed by the high-side reduction gears 100 alone.
  • the output shaft 104 of the high-side reduction gear 100 and the output shaft 204 of the low-side reduction gear 200 the high-side second internal gear 114 and the low-side second internal gear 214 , the high-side carrier 106 and the low-side carrier 207 , the high-side first planetary gear 108 and the low-side first planetary gear 208 , and the high-side second planetary gear 110 and the low-side second planetary gear 210 are used commonly, not all of these components need to be used commonly.
  • a commercially available series of reduction gears generally includes a plurality of reduction gears having different reduction ratios for each frame number (classification of types based on the size or transmissible torque, etc.). Accordingly, it is not necessary for a series of the invention to apply the invention to all the frame numbers, and in some cases, it is sufficient to apply the invention to a part of frame numbers.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
US10/400,063 2002-03-27 2003-03-27 Reduction gear and product group of reduction gears Abandoned US20030216213A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002-88566 2002-03-27
JP2002088566A JP2003278849A (ja) 2002-03-27 2002-03-27 減速機及び減速機のシリーズ

Publications (1)

Publication Number Publication Date
US20030216213A1 true US20030216213A1 (en) 2003-11-20

Family

ID=28449460

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/400,063 Abandoned US20030216213A1 (en) 2002-03-27 2003-03-27 Reduction gear and product group of reduction gears

Country Status (4)

Country Link
US (1) US20030216213A1 (zh)
JP (1) JP2003278849A (zh)
CN (1) CN1247916C (zh)
DE (1) DE10313947A1 (zh)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060243259A1 (en) * 2005-04-28 2006-11-02 Hks Co., Ltd. Supercharger
FR2926866A1 (fr) * 2008-01-25 2009-07-31 Valeo Embrayages Dispositif de reduction de vitesse de rotation entre deux arbres.
WO2010055228A1 (fr) * 2008-11-17 2010-05-20 Jean-Marc Baggio Réducteur à deux axes de sortie coaxiaux
US20150012994A1 (en) * 2004-06-29 2015-01-08 Damaka, Inc. System and method for concurrent sessions in a peer-to-peer hybrid communications network
CN104747658A (zh) * 2015-03-06 2015-07-01 吴小杰 零回差渐开线少齿差减速机
US20180119778A1 (en) * 2015-05-20 2018-05-03 South China University Of Technology Transmission method and device for coaxially outputting autorotation and revolution
CN108386491A (zh) * 2018-04-13 2018-08-10 浙江凡左科技有限公司 一种等线速减速机
US20180372189A1 (en) * 2016-03-15 2018-12-27 CISDI Engineering Co., Ltd Smart Self-Adaptive Planetary Transmission Device With Small Tooth Number Difference
CN111601984A (zh) * 2018-12-30 2020-08-28 罗灿 双内齿圈变线速行星排均衡减速器
US20200278009A1 (en) * 2019-02-28 2020-09-03 Lear Corporation Gear assembly
CN112780728A (zh) * 2021-01-07 2021-05-11 重庆大学 圆柱环槽式双摆线少齿差行星减速器
US11028918B2 (en) * 2018-03-16 2021-06-08 Bühler Motor GmbH Planet gear carrier for an epicyclic gear train and series of epicyclic gear trains

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5696340B2 (ja) * 2010-10-06 2015-04-08 日本電産シンポ株式会社 シートシャッターの駆動装置
CN104074929B (zh) * 2013-03-29 2016-05-25 住友重机械工业株式会社 减速机系列
CN108223700A (zh) * 2016-12-15 2018-06-29 行安机电股份有限公司 结合马达的减速装置
CN106641111B (zh) * 2016-12-19 2019-02-26 扬州大学 一种弧齿摆线行星齿轮减速器
JP6811634B2 (ja) * 2017-02-10 2021-01-13 住友重機械工業株式会社 遊星歯車装置
CN106969105A (zh) * 2017-05-24 2017-07-21 北京龙微智能科技股份有限公司 传动装置、包括该传动装置的立体车库和交通工具
DE102020201340A1 (de) * 2020-02-04 2021-08-05 Aktiebolaget Skf Modulare Hochgenauigkeitsgetriebeanordnung
JP7550665B2 (ja) 2021-01-26 2024-09-13 株式会社日本製鋼所 給電装置

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2955487A (en) * 1957-12-19 1960-10-11 Raymond B Malley Speed reducer
US3453907A (en) * 1967-01-30 1969-07-08 Aisin Seiki Planetary gearing
US3705522A (en) * 1971-06-30 1972-12-12 Gen Motors Corp Speed change mechanism
US4280376A (en) * 1979-05-17 1981-07-28 Energistics, Inc. Planetary gear system and gears therefore
US4850247A (en) * 1984-02-16 1989-07-25 David Yu Y type planetary gearing
US5326334A (en) * 1991-06-26 1994-07-05 Ra Jong O Continuously engaged geared automatic transmission with controlling brakes
US5484345A (en) * 1992-10-15 1996-01-16 Sumitomo Heavy Industries, Ltd. Compact gear reducer for rotation through an angle in either directions
US5695425A (en) * 1995-01-06 1997-12-09 Teijin Seiko Co., Ltd. Outer tooth profile of planetary gear apparatus
US6123640A (en) * 1996-01-27 2000-09-26 Zf Friedrichshafen Ag High reduction planetary gear with intermediate shafts
US6231469B1 (en) * 1997-12-11 2001-05-15 Teijin Seiki Co., Ltd. Internally meshing planetary gear device
US20030022751A1 (en) * 2001-07-27 2003-01-30 Comau Spa Robot articulation
US20030036455A1 (en) * 2000-01-21 2003-02-20 Kenichi Ushikoshi Gear apparatus
US6811514B2 (en) * 2002-01-23 2004-11-02 Axletech International Ip Holdings, Llc Electronic drive unit assembly for heavy duty vehicles

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2955487A (en) * 1957-12-19 1960-10-11 Raymond B Malley Speed reducer
US3453907A (en) * 1967-01-30 1969-07-08 Aisin Seiki Planetary gearing
US3705522A (en) * 1971-06-30 1972-12-12 Gen Motors Corp Speed change mechanism
US4280376A (en) * 1979-05-17 1981-07-28 Energistics, Inc. Planetary gear system and gears therefore
US4850247A (en) * 1984-02-16 1989-07-25 David Yu Y type planetary gearing
US5326334A (en) * 1991-06-26 1994-07-05 Ra Jong O Continuously engaged geared automatic transmission with controlling brakes
US5484345A (en) * 1992-10-15 1996-01-16 Sumitomo Heavy Industries, Ltd. Compact gear reducer for rotation through an angle in either directions
US5695425A (en) * 1995-01-06 1997-12-09 Teijin Seiko Co., Ltd. Outer tooth profile of planetary gear apparatus
US6123640A (en) * 1996-01-27 2000-09-26 Zf Friedrichshafen Ag High reduction planetary gear with intermediate shafts
US6231469B1 (en) * 1997-12-11 2001-05-15 Teijin Seiki Co., Ltd. Internally meshing planetary gear device
US20030036455A1 (en) * 2000-01-21 2003-02-20 Kenichi Ushikoshi Gear apparatus
US20030022751A1 (en) * 2001-07-27 2003-01-30 Comau Spa Robot articulation
US6811514B2 (en) * 2002-01-23 2004-11-02 Axletech International Ip Holdings, Llc Electronic drive unit assembly for heavy duty vehicles

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150012994A1 (en) * 2004-06-29 2015-01-08 Damaka, Inc. System and method for concurrent sessions in a peer-to-peer hybrid communications network
US9497181B2 (en) * 2004-06-29 2016-11-15 Damaka, Inc. System and method for concurrent sessions in a peer-to-peer hybrid communications network
US20060243259A1 (en) * 2005-04-28 2006-11-02 Hks Co., Ltd. Supercharger
FR2926866A1 (fr) * 2008-01-25 2009-07-31 Valeo Embrayages Dispositif de reduction de vitesse de rotation entre deux arbres.
WO2009095585A3 (fr) * 2008-01-25 2009-10-08 Valeo Embrayages Dispositif de reduction de vitesse de rotation entre deux arbres
WO2010055228A1 (fr) * 2008-11-17 2010-05-20 Jean-Marc Baggio Réducteur à deux axes de sortie coaxiaux
FR2938621A1 (fr) * 2008-11-17 2010-05-21 Jean Marc Baggio Reducteur a deux axes de sortie coaxiaux
CN104747658A (zh) * 2015-03-06 2015-07-01 吴小杰 零回差渐开线少齿差减速机
US20180119778A1 (en) * 2015-05-20 2018-05-03 South China University Of Technology Transmission method and device for coaxially outputting autorotation and revolution
US10663038B2 (en) * 2015-05-20 2020-05-26 South China University Of Technology Transmission method and device for coaxially outputting autorotation and revolution
US20180372189A1 (en) * 2016-03-15 2018-12-27 CISDI Engineering Co., Ltd Smart Self-Adaptive Planetary Transmission Device With Small Tooth Number Difference
US10767737B2 (en) * 2016-03-15 2020-09-08 CISDI Engineering Co., Ltd Smart self-adaptive planetary transmission device with small tooth number difference
US11028918B2 (en) * 2018-03-16 2021-06-08 Bühler Motor GmbH Planet gear carrier for an epicyclic gear train and series of epicyclic gear trains
CN108386491A (zh) * 2018-04-13 2018-08-10 浙江凡左科技有限公司 一种等线速减速机
CN111601984A (zh) * 2018-12-30 2020-08-28 罗灿 双内齿圈变线速行星排均衡减速器
US20200278009A1 (en) * 2019-02-28 2020-09-03 Lear Corporation Gear assembly
US10830310B2 (en) * 2019-02-28 2020-11-10 Lear Corporation Gear assembly
CN112780728A (zh) * 2021-01-07 2021-05-11 重庆大学 圆柱环槽式双摆线少齿差行星减速器

Also Published As

Publication number Publication date
DE10313947A1 (de) 2003-11-20
JP2003278849A (ja) 2003-10-02
CN1447043A (zh) 2003-10-08
CN1247916C (zh) 2006-03-29

Similar Documents

Publication Publication Date Title
US20030216213A1 (en) Reduction gear and product group of reduction gears
US11994195B2 (en) Transmission, powertrain, and vehicle
US20240262175A1 (en) Transmission and vehicle with transmission
EP1914444B1 (en) Reduction gear
US5692989A (en) Self aligning planetary gear transmission & speed reducer
JPH08240254A (ja) 電気自動車用動力伝達装置
EP2068036B1 (en) Reduction gear
CN101260929B (zh) 车辆行星齿轮装置
JPH07119801A (ja) 変速装置およびその組付方法
JPH05248517A (ja) 自動車の歯車式変速装置における伝動軸の軸受装置
US20130231213A1 (en) Transmission with double-sun, annular gear, and outer gear coplanar gear set
US7828687B2 (en) Modular planetary gear assembly and drive
JPH09296850A (ja) 減速装置
EP0775849B1 (en) Transmission including planetary gear sets
EP1903255A2 (en) Automatic transmission
EP0441144B1 (en) Improvements in epicyclic reduction gears
US5816972A (en) Transmission with simple planetary gear sets
EP1498641B1 (en) Differential gear device for vehicle
HUT54782A (en) Gear drive
JPH10227339A (ja) 副キャリヤ盤のない遊星歯車装置
JP2004270736A (ja) 遊星歯車装置の潤滑構造
EP1522768A2 (en) Differential gearing for vehicle
JP3078973B2 (ja) 変速機
JPH084846A (ja) ギヤドモータのシリーズに用いられる変速機
JP3116630B2 (ja) 自動変速機用歯車変速装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: SUMITOMO HEAVY INDUSTRIES, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:YAMAMOTO, AKIRA;REEL/FRAME:014334/0609

Effective date: 20030609

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION